Hydraulic system for obtaining automatic motor speed controls



":Iuly'2 2, 21952 G MATHEYS 2,603,950

HYDRAULIC SYSTEM FOR OBTAINING AUTOMATIC MOTOR SPEED CONTROLS Filed Feb /17, 1948 7 Sheets-Sheet l l/VVENTOR 6/15 ro/v N/r THEYS July 22, 1952 G. MATHEYS ,9

HYDRAULIC SYSTEM FOR OBTAINING AUTOMATIC MOTOR SPE ED CONTROLS Filed Feb. 17. 1948 7 Shets-Sheet 2 INVENTOR. 64570 M/IT/IfYf July 22, 1952 MATHEYs 2,603,950

G. HYDRAULIC SYSTEM FOR OBTAINING AUTOMATIC MOTOR SPEED CONTROLS Filed Feb. 17. 1948 7 Sheets-Sheet 3 INVENTOR. G43 ro/v M/IT'HEY5 B Y y 22, 1952 G. MATHEYS 2,603,950

HYDRAULIC SYSTEM FOR OBTAINING AUTOMATIC MOTOR SPEED CONTROLS Filed Feb. 17. 1948 "7 Sheets-Sheet 4 mg I July 22, 1952 MATHEYS 2,603,950

HYDRAULIC SYSTEM FOR OBTAINING v I AUTOMATIC MOTOR SPEED CONTROLS Filed Feb. 17. 1948 7 Sheets-Sheet 5 F/Gj MENTOR Gmroiv N/ITHEY5 BY v July 22, 1952 e. MATHEYS 2,603,950

- HYDRAULIC SYSTEM FOR OBTAINING AUTOMATIC MOTOR SPEED CONTROLS Filed Feb. 17.. 1948 7 Sheets-Sheet 6 6/15 m/v NHTHEYS BY ,zr

July 22, 1952 Filed Feb. 17. 1948 MATHEYS 7 Sheets-Sheet 7 q 1/ x I T/ 777 W MB m 4 H[\\ v Patented July 22, 1 952 OFFICE f HYDRAULIC, sYs'rEM FOR OBTAINING JHAUTOMATICVMQTOR SPEED CONTROLS 7 1 Ga'ston-Matheys, Brussels, Belgium ,iApplication February 17, 1948, Serial No. 8,98Q 1 j ,1 In Belgium Februarylil, 1947 r This e es testes i to hydraulic eta/or,

pneumatic regulators, pa'iticularly'for toolmachines, which show numerous advantages when compared withjmech'anicalj controls. Among other advantages softer movements, suppression of shocks, which are unavoidably brought about by gearings, even' those with carefully finished surface, flexible, control, 1 simplicity in construction 'owing'to the omission of complicated transmissions, precisionv and handines's, andlast, in case it is rationally designed, amoreleconomical cost 'thanthat of a mechanicalire'gulator, may be mentioned.

In spite of all advantages inherent tothehydraulic control, its general use, is not found in the past due to the requirements forthe regulationsbf machine tools, which are'particularly critical for drills, boring-machines, lathes and the like. 'These requirementsfl'may be'stated as follows: The working 'andfrjetractionspeed for the tools' 'must be sufficiently highj j(l3 to 20 yards/min.) to reduce" to" a'"minimum"'anyloss it qiclsi ts. (01. 60-52) connected with said return conduit and with the variableness' of the'jil'npo'rtance'of' the tool, its

number of revolutions/minute, as well as of the mechanical characteristics of the material to be Worked. g 7

Some known hydraulic regulators proposed to overcome these difficulties by; using pumps at several stages, the output'of which pumps varies in accordance with the use ofcomplicatedcams, rods, etc. Others use awhole net-w'orkioffconduits in balancing and compensating containers which are expensive and dimcult tooperate. Still others, order to secure precision in the workingstroke, control the flow of the fluid by providing a valve in the conduit and using additional conduits from'the source to a 'by-pass,

chamber of the servo-motor, a third conduit which connects the distributing and reversing valve with the other chamber'of the servo-motor. The last mentioned member comprises a plurality of valves which are equipped with manually operated controls and operate automatically under the combined action of springs and of diaphragms subjected to pressure variations, occurring at the different operativestages in said conduits. During the approach of the motor piston toward the work underlightload, said return conduit is closedwhilethefeed conduit is completely opened so that the cylinder of the servomotor receives the maximum output of the pump and so that the piston in the servo-motor and, thereby, the tool speed is asgreat as possible. In order to close said conduits during the working stroke, in a predetermined manner, so as to evacuate the excess of the fluid and tolimit the feed towards the working'chamber to the exactly required quantity, these conduits and their valve means provide the means for obtaining the'most favorable speed for the piston and the tool, in accordance with the operating conditions. During the retraction of the piston; the said conduits are opened in full in order to evacuate as rapidly as possible, the fluid contained in the cylinder of the servo-motor and to feed completely the chamber opposite the working chamber, in

- order to'provlde the greatest possible return speed whichrequires the application of "particularly powerful motorsfor the operationof pumps, which must work continuously at highest pressure and capacity, even when the real power, produced in the servo-motor, is only absorbing asmall part of it.

It is one object of the present invention to provide an automatic diiferential regulator for the speed transmission of hydraulic and/or pneumatic controls, particularly for machine tools, which comprises a feed conduit from the 'fiuid source, and a return conduit connected to said feed conduit between a' distributing and reversing valve and the working chamber ofa servo-motor returning the fluid to said'source, fandi a member ofthetool. I

It is another object of the present invention to confer to the tool an accelerated speed during its feeding stroke from the top downby means Of a supplementary conduit leading from the working-chamber of the servo-motor, directly to the tank contai ingthe fluid and a check-valve inserted in'this supplementary condu'it, which thus permits by opening of said check valve the direct feed of fluid -to the working chamber, in order to compensatefor the vacuum which appears when, during said feeding course,

the tool and the pistonlof the. servo-motor fall,

vertically at an accelerated speed, owing to the combined effect of their weight and the use of the full output ofthe pump; said speed being greater than the one corresponding to said full output. ll It is a further object of the present invention to provide accelerated speed to the too 1,'during its feeding course, while moving, in another than downward direction, by means of a compression spring disposed in the; working chamber, the expansion action of whichgadds ilduring said'ffeedmal working-chamber, a valve operati its normal piston, a small pist'dn; high passes,

through the former, reciprocates'ina second 7 working-chamber, disposed in the hgllcwrod oi hteu h the normal piston and separated from a conduit connected with'the second working chamber, while a supplementary valve is asseciated with said first one, working under the comhined action of a diaphragm and a piston, at the same time upon a coriduit to thecfirst 'tvork-' ing chamber and s an a'cond ui tj leading from the supplementarylvalve' toftheflu'idtank, in such a manner'that curing the feeding course of the tool, said supplementary valve is connectedwith the first worlging chamber and to the conduit connecting.'the' supplementary valve to the tank, 2,1 lowing thus the feed of fluid 'necessa'ry fto com pensate the-vacuum c'reatedlby the normal piston, whilegoingldownwards" an accelerated speed, under'the combined action: o'i its own weight and theffull output of the pump; 1 j- I f It is yetanother obj ct of the present invention to provide a variationfef this last modification by,insertingfafcompr' onQspring in' said first working chamber, so that} sfaction adds to that of thef ull outp' tof 'the fliiidti n' order to give the piston of the 'se'rvo motor and the tool, when moving in another direction than vertically down,

duringthefeeding course, the required accelereteq. gged;';.,. .7 1

With .these and other objects in view which Will become apparent "in thfollowing detailed description, whichdiscloses several examples. of the present invention particularly 'adaptedte an hydraulic and/ or pneumatic'regulator, as disclosed n't -a ia ten uoq t tt pre nvention will be;clearly'understgodfin connection w h h ttteme ny ad a ngs I w i h Figure]. isa sectionfl elevationIof one embodiment of the regulator;' i Y Figure 12 is a schematic diagram of the regula tor, thev servo motor and theirlcombination .with the conduitsystemi 3 is a variation of the schematic diagram shown in Fi'g, 2; i

Fig. 4 is a sectional elevation of another embodiment of the regulator; v V

Fig. 5 is still another variation of the schematic diagram'shown in Fig. 2; j

Fig. 6 is asectional elevation of the embodiment of the regulator shown in Fig. l 'in connection with a servo-stabilizeryand 7 is a sectional elevation of the regulator together with the conduit system, substantially as shown inFig.

Referring now to the drawings end particularly to 'Figs.1 and 2, the regulator in the first embodiment comprises a cylinder 1 receiving a piston valve 3, therod of which carries a diaphragm 11, which by means of a spring 12, acting as static equalizer, presses against the corresponding wall of abody 2 Thisjpiston 3, dueto its position which is determined and controlledbyqthe dia phragm I'Lcloses circular slots 4 provided in the The body ZcOhtains a c cylinder I, thus connecting or disconnecting the conduits A and A1, terminating in the cylinder l. The conduit A is connected with the conduit E (Fig. 2), supplying the chamber T1 of a servomotor with fluid, while the conduit Al is connected with the fluid tank Z and serves the purpose of returning the fluid -.to,the,t ank Z,

haml t: 2 wh ceives one end of a conduit E, the other end of which terminates into the chamber T of the servo-motor. From the chamber 22 extends also a chahheliii fi -as well as a channel 38, which in I turn-receivesone'end of a channel 20 the other is subjected to theaction of the fluid pressure prevailing in the conduit E and in the chamber 22, whilecits other face is subjected to the action of tne'ifluidjpr sure' prevailing in he conduit A. "A'sp' ine 'l l. dispose IQn he valvefi. the action of which is described below, maintains the diaphragm 1 in a position;providing a complete opening of the valve 8, permitting free passage from the chamber 22 to the channel 38. v The channel It is equipped at the farther and from the chambenzzf witha slot '39 which communicateswith' the diaphragm "and a byepass slot 'lfldisposed oppositelythe slot 39, communicates withthe' channel 20.j"The slot I8 maybe closed by means of the valve l9, operated by the handle as. v

The regulator werks, in the following manner: When the distributing iahd reversing valve D is positioned to direct fluid to flowthrough the con-. duit Binto' the chamber Ti'of theservo-motor, this fluid operates the'piston X thereof imparting to it a downward stroke; (Fig."'2) and driving out the fluid contained in the' chai'nbe'r T of the servomotorthrou'gh the conduiiiE, the chamber 22 and the'channels 38,20 and'cdnduit E1; A certain amount. of fluidflcan escape through th'e'conduit l6, and'the s'let I8,which thevalve 19 opens to a predeterminedextent. ,Thepiston X ofthe servo-motor encou sno resistance and is thus moving at a spee rrespondin to the total capacity of the pump'R' The pressure. in. the chamber 22 of the diaphragm Twill, 'invie'w of the spring 'l'l, maintain thediaphragrri ,l and the valve'8 in'ia position or equilibrium as shown in'Fig. 1', thus allowing therapid discharge of the chamber. T throughthel'cohduitsEand' the other channels" {connected thereto. Duel I to the fact thatftheiflow' Oi the, fluid takes place freely, the pressure in the channel 16 is notrsuificient to operate the diaphragm l1, and, thereby tomove the piston valve 3; and thusffthe r1 11 output'fof the fluidprovided by the pump? is used for exerting the stroke of the piston}; of the servoeniotor. Asisoon as the piston-X or the tool on which it is acting meets any resistance, the. need for more pow'er arrives. The pressure in. the chamber T1, the conduit B and inv the conduit, A increases and pushes the diaphragm I and the. valve 8 to the right, (Fig. l), interrupting'the connecij ionbetween the Ychamber 22] and the channel 381 through the valve .8, "The'fluid released from the chamber T of theservbemotor can then only escape through the channel 16 and the sl t 18 i h" s .on v partially c s y means otthe Valve 19', which was previously regulated by the, knob 36 in such manner-that theoperating oo possesssli g, e ui d ec d for the est'wlorlsing'conditio'n's. The output of the pump re mains however thesamfandthe piston X has, a tendency Ito "rediicej its initial ,s'p'eedfj thu's -the pr(assume 'in' 't'he'char'fnber 'r,' the con uit; m and the ehan e1"ls mcreases' proportiona ely to t e resistance the fluid hasjto'fsurmount inforder to pass through the calibratedslotllfl. Thispressure is'acting jat th'e'same timeiupon thje'diaphragm I1 and pushes'it downwardly from the position illustrated in Fig. 1 and; thereby; also thepiston 3, which, opens the slots 4 establishing th'us connection'between the conduits A and- 1, so that a certain quantity of 'fluid passes through the thus created by-pass, reducing the pressure prevailingin' the chamber Trand motion of "the pist'onithe stroke speed of which is hereafter reduced accor'dingjjtd'th'e amoun of fluid escapingthrough the'slot 18." The pre'sfsurepre- 'vailing in the chamberT, the conduit El and the channel I6 decreasesjconselquently, which allows the compensation-spring l2; previously setfac; cording to the respectivesection's 'of the several conduits, to driveback the piston valve 3fandthe diaphragm IT to their initial positions;' causing thus a closing of the by-pass slot'lj'to a certain extent, depending upon the strokespeed of, the piston X and the different effects resulting therefrom. v

. When, at the required moment, predetermined by the position given'to the controlling organs 23 and 24 operated 'by the'piston X '(Fig. 2) the distributing and reversing valve D stops the working stroke ofthepiston X and'starts'retraction of the piston X, the fluid is caused to flow through the conduit E1 to the channels 20 and '38, acts upon the corresponding'face'of the valve 8 and, cooperating withthejfsprinlgll l, pushes the valve 8 and the diaPhragmfI'back to'the original position shown in Fig. 1; thus "clearing the way for passage of. the fluid into the chamber 22, the conduit IE1 and thefchai'riber'T of the servo-motor.

On the other hand, as "inits opposite course, the

piston X has to overcome the resistance of the fluid acting" on the'other face of the p'istonX. A certainpressure will occur in thecha'mber T of the servo-motor and in all conduits connectedfthereto, asZwellfa's in the-channel lfi, as result of which the diaphragm]? will be pushed back; the diaphragm I1, operating on the piston valve 3, causes opening of the slots 4, thus allowing anadditional'amoiiht of "fluid to escape through-the conduits A and "A1, and to accelerate the retractionof the piston X.

It is clear that if, during the working stroke of the piston X, the load would momentarily disappear, the rapid speed of the stroke would be automatically and immediately reestablished bythe interference of the above described organs, and the contrary effectwould also automatically appear as soon as the load wofild befeltagain. Fig. 3 represents a variation of theembodiment shownin Fig. 2, according to which'it' is possible to give to the tool and to the piston jointed thereto, duringits rapid advance'under no load, an, accelerated speed which is greater than the pne resulting from the maximum output of the pump P 1 l a If this rapid advanceunder no load 'takes'place' from top to bottom,.it wil1 be sufi'icient to provide a supplementary .co'nduitfCf (Fig. 3)whichconnects the working chamber'Tr'of the servomotor with the fluid tank Z in which case a check-valve 3 3" is inserted in this conduitC.

When the distributing'and reversing valve D is positioned to direct fiow'ofthe'fididftojthe ch mber i ou se ss tar ?were T communicates with the fluidremoving conduitsfand the piston Xis'performing' its downward stroke under the combined action of the fluid pressure, introduced by means of the 'conduit B and its own weight. The piston X passes in its" rapid stroke'a bigger volume than that which' can be replaced by'the fuel capacity of the pump, crea'tinga vacuum which causes. the opening'of the check-valve 33 and allows thus the refilling'from the tank'Z through theconcreated vacuum spacef'Thus the feeding movement of the tool will automatically continue at a greater speed than that corresponding tothe' f illcapicity of'thefpump, I

in case therapid advance-under no load takes place in another than the downward direction; it willsuflice'toprovide a compression'spring 'the working chamber Trof the'servo-motor,

as shown' in Fig. 3, the action of which spring plis'hes the piston X during" its .rapid advance under. no load, adding its effect to that of the full capacity of the pump P, whereas the conduit 0 and it'scheck valve 33' allow the feed of the fluid necessary to fill the vacuum, caused by the displacement of the pistonX at an accelerated speed which'displacement is greater than can be supplied by the fuel output of the pump P in the same time period. p

e .The Figs. 4 and '5 represent another embodiment of the regulator in accordance with the invention; which permits of an accelerated speed for the tool duringits'rap-id advance under no load superior to e jone which can be achieved with, the pump P working at full capacity. In this embodiment, [the regulator of Fig. ,1 is equipped'with supplementary elements, and the conduit system disclosedin Fig. 2is'modified in the follgwing manner:

"A "member 30'is added to .the body 2, which member 30 has,in'jaddition todiaphragml', a diaphragm 3| which operates piston valve 3.2, adapted to reciprocate in the cylinder 40, and connected on one side by means of the slot 33 with a conduit F, which terminates 'in the chamber'Tr of the servo-motor, and on the other side, respectively, by means of the slot 34 with a conduit Cterminating in the fuel tank Z, and by means 'of'theJslot 35 withthe conduit B which providesconnections with the conduit B." The cylinder I, as previously described.

'I' lhe'cylinder of the servo-motor contains, in addition to the} piston X, a, second piston'X which is received by the cylinder Y formed in the hollow rod of the piston X. The conduit B connects the hollow rod of the piston X" with the distributing andreversing valve D. If the piston X is. disposed in' such manner that its vertical downward coursecorresponds with the working stroke, it may, during its rapid advance vunder no load, obtain an accelerated speed, under the combined action of its own weight and of the full capacity of the pump P, in which case the spring K (Fig. 5) is'not used. But, if the piston and the tool execute their rapid advance under no load in another than the downward direction, their weight does not accelerate the speed during rapid advance under no load; in warmt ceme ie s i K s s e erator to the said'cylind'er, a fluid diverting'com duit leading from the working end of said :cyl-j inder to the said'tank, first valve means disposed in the said fluid diverting conduit' and adapted to shut-ofi',.the latter,. an exhaust fluid conduit leading from the exhaust side of the said cylinder to the said tank, second valve means disposed in the said exhaust fluid conduit and adapted-to shuteoihthelatter, firstmeans, responsive above a predetermined pressurein the said exhaust fluid conduit .for openingihe said first valve means in the said fluid diverting conduit, and second means responsive above a predetermined pressure in the said fluid divertingconduit for closing the said second valve means-in one said exhaust-fluid conduit. 1 h 1 2. The device, as set forth in claim Lwhich-includes a manually set throttling device disposed in said exhaust fluid conduit in parallel arrangement with the said secondvalvemeans, thus permitting escape of exhaust fluid at a reduced .pre-

determined volume uponclosingv the said second valve means.

3. An automatic differential hydraulic regulating device to act upon the volumetric admission of fluid under pressure in a hydraulic cylinder, comprising a cylinder adapted to receive fluid under pressure, a piston reciprocating in said cylinder, :an exhaust conduit leading from said cylinder, a valve disposed in said exhaust line, a spring tending to maintain said valve in open position, said valve being adapted to shutoff said exhaust conduit partially only, a first pressureresponsive actuator operating said valve against pressure of said spring in response to pressure variations in said cylinder, a manually set rigid throttling device disposed in said exhaust conduit, a chamber disposed in said exhaust conduit between the said cylinder and said throttling device, a second pressure-responsive actuator disposed in said chamber, a fluid pressure generator having constant volumetric output, afluid ad: mission conduit between thesaid fluid pressure generator and the said cylinder, a flow reversing device in said admission conduit, a fluid diverting conduit leading from the said admission conduit between the said cylinder and said reversing device, a movable piston valve disposed in said diverting conduit and operated by the said second actuator to act as by-pass for the working fluid, a spring tending to counterbalance the said piston valve against the said second actuator, the latter being responsive to pressure variations in the exhaust conduit.

4. An automatic differential hydraulic regulating device to act upon the volumetric admission of flu d under pressure in a hydraulic cylinder, comprising a cylinder adapted to receive fluid under pressure, a piston reciprocating in said cylinder and dividing the latter into a working chamber and an exhaust chamber, an exhaust conduit leading from the exhaust chamber of the said cylinder, 2, housing interposed in said exhaust conduit, a movable shut-off valve disposed in the said exhaust conduit, a rigid manually set throttling device disposed in the said exhaust conduit within the said housing, a first pressureresponsive actuator secured to the said shut-off valve to operate the latter, a spring disposed on the side of the said shut-off valve opposite to the said first actuator to exert a constant pressure on said valve to inaintaini the open positi'onaof said shut-on? valve and to oppose the action of the working fluid 'pressure' exerted against' the *said first actuator," a tank adapted f'toreceive the fluidya fluid pressuregenerator having constant :volum'etric' output, a connecting conduit leading from the said tankitothe said-fluid pressure generatona flow reversing device; the portion of the said exhaust conduit'leading' from the said'housing connecting the said exhaust fluid outlet channel with the said reversing-devica-a further exhaust conduit leading fromthersaid reversing 1 device toi'the said fluid tank, aworkingfluid'conduit leading-from the'said i fluid pressure; generator to the said reversing devicer-andi'fromthe latter to-the working chamber-of 1the ;said cylinder, a fluid; diverting conduit extendingfrom the said:working fluid conduit :bet'weenithe said cylinder and the said reversing :deviceinto the 0 said -housing,-=a workingfluid channelfdisposedin the said housingxand receiving the said fluid diverting -;conduit, a first. working fluid exhaust chamber disposed: inthesaid housing and; the

,said working fluid channel of-the latter leading into the said last-:mentionedchamber, 'a sleeve inserted into the said last-mentioned chamber of circular groove, a movable piston valve sliding in the said sleeve, a second pressure-responsive actuator secured to the said piston valve to operate the latter, a back-pressure chamber opening upon the said second actuator and communicating with the said exhaust fluid inlet channel, a spring at the other end of the said movable piston valve adapted to exert a constant pressure upon the latter and to balance back-pressure variations in the said back-pressure chamber exerted against the said second actuator, a second working fluid exhaust chamber disposed in the said housing and surrounding the portion of the said sleeve having the said circular groove, the said piston valve permitting connection and disconnection, respectively, between the said first and said second working fluid chambers depending upon the position of the said piston valve in the said sleeve,

a working fluid outlet channel extending from the said first working fluid chamber and'a working fluid outlet conduit leading from the said working fluid outlet channel to the said tank, a third working fluid chamber disposed in the said housing and opening into the said working fluid diverting conduit, the said first actuator opening into the said last-mentioned/chamber to act upon the said shut-off valve in accordance with the working fluid pressure variations prevailing in the said diverting conduit.

5. An automatic difierential hydraulic regulating device to act upon thevolumetric admission of fluid under pressure in a servo-motor, comprising a first cylinder, a hollow piston in said first cylinder, said hollow piston forming a reciprocating second cylinder, a stationary second piston received by said reciprocating second cylinder of the first piston, a fluid tank, a fluid pressure generator having constant volumetric output, a first working fluid conduit leading from the said tank through the said generator into the said second cylinder for feeding pressure fluid from said generator to the said second cylinder, a fluid diverting conduit leading from the said second cylinder to the said tank, flrst valve means disposed in the said diverting conduit and adapted to shut ofithe latter, an exhaust fluid conduit leading from the exhaust end of the said first cylinder to the said tank, second valve means disposed in; thesaid exhaust flu id oonduitj'and said first working :fluid conduit to the said second working 'fiuid'c'onduit; third valve means disposed in the said first connecting fluid conduit and adapted to connect the latter to the tank and to'the said second. connecting fluid conduit, respectively, first means responsive above a predetermined pressure the said exhaust fluid conduit for openingth'esaid first valve means in the diverting conduit and to connect the latter to the tank, secondfmeans responsive above a pre determined pressure in the said diverting conduit for closing the said" second valve means in the said exhaust fiuidconduitfand third means 'responsive above a predetermined pressure in the said diverting conduit for operation of the said third valve means and, thereby, to connect the working side of the said first cylinder to thesaid working fluid conduit and the tank, respectively, depending upon the pressurein the said diverting conduit. j r Y 7 6. The device, as set forth in claim 1, which includes a helical spring disposed in the said cyl- I2 inder on the working side of the said piston, in order to accelerate the working speed of the said pistonn v r '7. The device, as set forth in claim 1, which includes a third pressure-responsive means sercured to the said first valvemeans and responsive to the pressure difference between the pressure in the said diverting conduit and that in the said exhaust conduit. I GASTON MATHEYS.

REFERENCES CITED v The following references-are of record in'th file of this patentf H I UNITEDL'S TA'I 'ES PATENTS Number Name, o 1 Date 1,964,196 Cuttat June 26, 1934 2,071,781 Douglas Feb. 23, 1937 2,160,920 Strawn June 6, 1939 2,303,946 Miller Dec; 1, 1942 2,328,979 Herman et a1 Sept. '7, 1943 2,328,980 Herman et a1. Sept. 7, 1943 FOREIGN PATENTS Number Country Date Great Britain June 2, 1932 

